Rotary pump



March 25, 1958 T. F, ESERKALN ROTARY PUMP e Sheets-sheaf. 1

Filed June 7, 1950 March 25, 1958 T. F. ESERKALN 2,827,857

ROTARY PUMP Filed June '7, 1950 6 Sheets-Sheet 3 INVENTOR. 7Ze0aore ffS/id/lr ,4 ffar/r ey March 25, 1958 T. F. EsERKALN ROTARY PUMP 6Sheets-Sheet 4 Filed June 7. 1950 March 25, 1958 'r. F. ESERKALN2,827,857

- ROTARY PUMP Filed June 7, 1950 6 Sheets-Sheet 5 IN V EN TOR.

7Z0dore Ffseria/n March 25 1958 T. F. EsERKALN 2,827,857v

ROTARY PUMP Filed June 7. 1950 6 Sheets-Sheet e INVENTORL Y K Tbadfllf[Berta/n BY United States Patent RO RY UMP Theodore F. Eserkaln,Wauwatosa, Wis.

pp cat on une 1950, Seria N 166,628

C a m l- 193-129) This in ent n e ates to pum and motors .and moreparticularly to a vane type device including a working C am e th apacityof wh h may be a t at w to a y t olumet ic displacement of the devicewhen used as a pump or to vary the torque when used as a motor.

Throughout the remainder of the specification; the device will bedescribed primarily as a pump but it is to be understood that the termpump also defines a motor, since the only difference between itsoperation as a pump or motor lies in the fact that as a pump it isdriven mechanically while as a motor it is driven by the application offluid :under pressure. The term vane" as used in this specificationis tobe construed as any element which serves to divide the working chamberof the pump into separate cylinders.

The primary object of the present invention resides in the provision ofa new and improved pump which has increased flexibility in performanceand application coupled with compact sine and increased mechanicaleflicicncy.

Another object of the invention resides in the provision in a pump ofnew and improved means for effecting the reversal of the direction offlow of the fluid output of the pump without reversing the direction ofrotation of the pump.

Another object of the invention resides in the provision of a new andimproved pump, of the vane type, in which the reversal of the directionof pump operation may easily be effected either while the pump is idleor in operation.

Another object of the present invention residues in the provision in arotary pump of a new and improved combination of elements which includea rotor, adapted to be selec ively driven in either direction, having ahollow cylindrical flange portion including a series ofcircumferentially spaced radial slots, and a plurality of cooperatingparts including a non-deformable enveloping element surrounding thehollow cylindrical flange portion of the rotor, a non-deformable memberhoused within the hollow cylindrical flange portion of the rotor, and'aplurality of vanes, disposed'for constant contact with the adjacentsurfaces of the non-deformable enveloping element surrounding the hollowcylindrical flange portion of the u and e ce-de rm b e member ho sedithin he hollow cyli drica fla ge p t on f. he otor, uided for al sl d nmo ment n the slots te med in the flan P r i n f he r o h n n rmableelement, nondeformable member and vanes being movable as a unit withrespect to the rotor for varying the volumetric displacement of thepump. I

Another object of the invention lies in the provision ina vane typerotary pump of new and improved means for varying the displacement ofthe pump selectively on either side of a neutral or zero displacementposition bythe arcuate movement of the rotor enveloping element2,827,857 Patented Mar. 25, 1958 p ,2 and its associated parts as a'unitwith respect to the axis of rotation .of the rotor.

Another object of the invention lies in the provision in a rotary pumpof a new and improved construction and arrangement of theparts of thepump which permits the several cooperating parts of the pump to berotated simultaneously at the same speed to thereby materially reducewear on the parts of the pump and also materiall increase the operatingetficiency of the unit.

Another object of the invention, relating more partieularly to the formillustrated in Figs. 16-19 of the drawings, lies in the provision ofcylindrical vane elements.

Another object of the invention, relating to the form of "the inventiondisclosed in'Figs. 16-19, lies in the construction and arrangement ofthe several parts of the ice 1 pump in a manner which permits theanchoring of either the rotor enveloping element or the member housedwithin the rotor against rotary movement, without imparing theefliciency of the pump operation or increasing wear on the cooperatingparts, due to rolling action of the cylindrical vane on the part whichmay be fixed against rotating movement.

Another object of the invention resides in the provision in a pump of anew and improved means for facilitating its connection into a workingcircuit by providing a plurality of inlet and outlet ports arranged forselective positioning with respect to the pump mounting bracket and foruse in making the desired pipe connections.

Another object of the invention resides in the improved construction ofthe device which permits it to function efficiently through a widerrange of speeds of rotation efficient and simultaneous operation of asingle vane in both chambers.

Another object of the invention resides in the positive positioning ofthe vanes in a manner which enables the unit to be operated selectivelyin either direction of rotation as either a pump or a motor.

Another object of the invention resides in the provision in a vane typepump of a new and improved combination of elements which cooperate in amanner to provide for the constant contact between the vanes and acooperating surface without requiring the use of either hydraulicpressure or yieldable mechanical means.

Another object of the invention resides in the formation of a curvedsurface on the vane adapted for constant line contact with a cooperatingsurface in a manner such that eccentric displacement of the vanecarrying rotor with respect to the cooperating surface will effect arocking movement of the line of contact between the vane and thecooperating surface from one position to vane carrier is altered withrespect to, the cooperating surfaces with which the vane contacts duringrotation of the vane carrier with the cooperating surfaces.

A further object of the invention resides in the provision in a vanetype pump of. a rotatably mounted vane carrier having an outercylindrical surface, a non-deformable element surrounding said vanecarrier having a cylindrical inner surface of a gerater diameter thanthat of the carrier and a non-deformable member disposed withinthecarrier having a cylindrical outer surface with the diameter smallerthan that of the cylindrical surface of the carrier; the radius of thenon-deformable member plus the diameter of the cylinder forming thecurved surface on thevvanesbeing equal to the radius of thecylindricalinner surface of the non-deformable element surrounding thevane carrier.

Another object of the invention, with reference to the modified form ofvalve disc shown in Fig. '12of the drawings, resides in the provision ofa new and improved arrangement whereby the substitution of the presentvalve disc renders the device capable of functioning as a compound pumpby directing the discharge of the outer pump into the intake of theinner pump.

Another object of the invention, with reference to the modified form ofvalve disc shown in Fig. 13 of the drawings, resides in the provision ofa new and improved arrangement whereby the substitution of the presentvalve disc makes it possible to utilize the discharge of each pumpindependently. I

Another .object of the invention, with reference to the single workingchamber pump shown in Fig. 14 of the drawings, resides in the provisionof a new and improved vane type pump particularly adaptable for use as amotor.

Other objects and advantages will become apparent.

from the following description of the illustrative embodiments of thepresent invention shown in the accompanying drawings;

In the drawings:

Figure l is .a vertical longitudinal sectional view through a pumpconstructed in accordance with the teachings of the present invention,as indicated by line 1-1 of Fig. 2.

Fig. 2 is a front elevational view of the pump showing means forselectively adjusting'the displacement of the pump and the direction ofrotor rotation and also showing the adjustable bracket, in dotted lines,for the purpose of facilitating the installation of the necessary pipingfor the hydraulic circuit in which the pump is connected;

Fig. 3 is a rear elevational view of the pump showing.

fragmentary portions of the hydraulic circuit and indi-. cating thegeneral arrangement of the ports in a manner to provide for any of amultiplicity of piping arrangements which are available by opening orblocking either of the inlet or outlet ports and making the pipingconnections conform with the most desirable arrangement for theparticular application at hand;

Fig. 4 is a vertical sectional view taken on the line 4-4 of Fig. 1showing the eccentric mounting of the positioning of the pump mounting.

3 invention be desired;

collector plate showing the inlet and Fig. ,8 is a front elevationalview of the distributor and outlet passages an associated porting,together with means for retaining the plate in a fixed relationship withthe pump casing;

Fig. 9 is a rear elevational view of the plate shown in Fig. 8 showingvthe porting which leads the fluid to and from the rotor chamber of thepump;

Fig. 10 is a vertical sectional view taken on the line iii-16 of Fig. 1showing the ports in the pump casing which are aligned with thecooperating ports in the distributor plate;

Fig. 11 is a vertical sectional view taken on the line 11-11 of Fig. 1"showing the inlet and outlet passages formed in the pump casing; thedotted lines indicating a modified form of the casing permittingindependent use of the two pumps;

Fig. 12 is a front elevational view of a modified form of distributorand collector plate showing fluid inlet and outlet passages and portingarranged in a manner to placethe two pumps in series connection whereinthe discharge of the outer pump is directed into the intake of the innerP p; r

Fig. 13 is a view similar to that shown in Fig. 12 showing a furthermodification of the distributor and col lector plate wherein thepassages and porting are arranged to permit the independent use of thedischarge of both of the pumps;

'Fig. 14 is a view, similar to that shown in Fig. 5A, showing a modifiedform of the present invention in which the pump is provided witha-single working chamber which makes-the device more readily adaptablefor use as a motor, should this form of application of the Fig. 15 is adiagrammatic view showing the movement of the line of contact betweenthe cylindrical surface on the vane-and the inner and outernon-deformable ring elements-of the pump; the full line showingsindicating the mean position wherein the respective radii of the driverpassed through the axial center of the vane and of the inner andouterrings at the line of contact between the vane and their respectivesurfaces are coincident, and the extreme position wherein the radii areseparated by the amount of eccentricity between the driver and thedisplacement adjusting means with respect to the center of rotation ofthe pump rotor;

Fig. 5 is an elevational view of the pump assembly with the coverremoved and showing the neutral or zero displacement position; v

Fig. 5A is a view similar to Fig. 5 showing the pump parts in a positionof maximum pump displacement in one direction of rotor rotation;

pump parts in a Fig. 5-8 is a view similarrto Fig. 5 showing the pump 1parts in a position of maximum pump displacement in the other directionof rotor rotation; v

Fig. 6 is a perspective view of oneof the vanes of the pump showing thearcuate configuration of the opposite surfaces of the vane which contactthe respective surfaces of both inner and outer ring elements;

Fig. 7 is a front elevational view of the pump rotor showing the guidemeans for the vanes and also the inlet and outlet porting for the fluid;

inner and outer rings; arbitrary intermediate positions being indicatedby the dotted line showing, for the purpose of more clearly illustratingthe'movementofthe line of-contact on: the curved surfaces of'the vanes.

Fig. 16'is a view similar to Fig; 5 with the pump parts inneutralposition but showinga modified form ,of the invention .in which thevanes are formed of cylindrical members adapted for rolling contactlwiththe surfaces with which they are in contact.

Fig. 17 is a view similar to that shown. in Fig. S-A incorporating themodified form of vanes and showing the parts in a position of maximumpump displacement in one direction of rotor'rotation;

Fig. l8'is a'frontelevationall' view of the pump rotor showing, theguide means .for the modified form of vanes together with the requiredinlet and outlet porting for the flow of-fluid to and from theworkingchambers of thepumpg and Q f .Fig. 19 'is a perspective view of one ofthe vanes used in the modified form of the invention;

Referring more. particularly to the drawings, it will he noted that thepump of the' present invention comprises a casing or housing 20,preferably in the form of a casting and including a pumpgrecess 21 andsuitable inlet and outlet eharnbers 22' and 23 respectively. A pluralityof concentrically arranged contiguous bores of different diameters serveto form an opening extending through the housing. Each of these boresserve a particular purpose and include a gasket recess 24, a rotorrecess 25,.a bear-- ing receivingybore 26,-: a shaft receiving bore 27and a collar receiving bore 28. a v a I he ee f t e o n so b t e strilis ti n e s est rs housing through the medium of a washer 31 and adeformable O-ring 32 positioned within the gasket recess 24. The pumphousing 20 is adapted to be attached to a mounting bracket 33 secured tothe end of the housing 20 opposite the cover 29 by means of cap screws34. The mounting bracket 33 includes an upstanding flange 35 throughwhich the cap screws 34 are passed and a flat base portion 36 adapted tobe attached to a supporting surface (not shown) in any approved manner.Referring more particularly to Fig. 3 of the drawings, it will be notedthat the arrangement of the cap screws 34 is such that the housing 20may be attached thereto selectively in either the position shown in fulllines, wherein the inlet nd outlet piping extends horizontally from thehousing,

or in the dotted line position, wherein the inlet and outlet pipesextend vertically from the housing. The selective I positioning of thehousing on the mounting bracket 33 is important as it provides a meansby which the connection of the pump into a hydraulic system is greatlyfacilitated due to the fact that the piping may be attached through thecasing in any one of a large member of cornbinations made availablethrough the selected positioning of the housing on the mounting bracket.Suitable holes 37 are formed in the base 36" to permit the passageofpipes through the base should the desired piping require thisarrangement.

' The rotor 33 which forms one element of the pump is housed within therecess 21 of the pump casing 20. The rotor 38 includes a shaft 39, adisc or plate portion 40 anda forwardly extending hollowcylindrical'fiange 41. With the rotor '38 properly positionedin thecasing 20, the end of the shaft 39 projects beyond the casing20 and themounting bracket 33 to provide a means on which any suitable drivingelement such as a pulley or gear (not shown) may be secured. The sourceof power for effect ing the rotation of the pulley or gearmay be of anyappropriate form such as an independent electric motor or any suitabledriven shaft adapted for transmitting power to rotate the shaft 39.- Theinner end of the shaft 39 is journaled for rotation in a roller bearing(t2, the outer race of which is pressed into the bore 26 formed in thehousing 20, While a ball bearing 43 retained in spaced relationship withthe roller bearing 42 by a spacer collar 44 serves as a second supportfor the shaft 39. The outer in turn is retained within the bore 28formed in the housing 20. In addition to serving as the impeller for thepump, the rotor 38 is proyided with the hollow cylindrical portion 41'which is divided into a plurality of sectors 46 by plurality of radiallydisposed slots 47 each adapted to receive and guide individual vanes 48.

race of the bearing 43 is pressed into a collar 45, which Each of thevanes 43 comprise a quadrilateral prism having a pair of parallel fiatsides 49 and a pair of convex sides 50. The convex sides 50 of thevanes'48 are formed by portions of the surface of a cylinder having adiameter substantially equal to the difference in the radii of the outercylindrical surface of a non-deformable member 51 and the innercylindrical surface of a non-deformable element 53 generated from alongitudinal axis positioned by the centers of the ends of the prism.Each vane has alength which is coextensive with the depth of the hollowcylindrical flange portion 41 of the rotor 38.

The inner convex surface 50 of each of the vanes 43 is arranged for linecontact with the outer cylindrical surface of a non-deformable ringmember 51; while the outer convex surface 50 on each vane 48 is arrangedfor line contact with an inner cylindrical surface 52 formed on anon-deformable element 53, preferably in the shape of a ring, anddisposed to surround the hollow cylindrical portion 41 of the rotor 38.The depth of the ring member 51 and the element 53 being identical withthe length at the va es eee e nee t e d a ng i in e lea l that w e thees 48 e e p s io ed w thin the l s A he Pe e 3% Wi h heir inn r surfeern seatact with the outer surface of the ring member 51 that the outersurfaces 50 of the vane provide a series of contacts along which theelement 53 may be slid into posi: tion during the process of assemblingthe pump. It will also be noted at this point that the non-deformableelse.- ment 53 is supported in concentric relationship with thenon-deformable member 51 by reason of the fact that each of the vanes 48have the identical diametric dimension so that any displacement of themember 51 with respect to the axis of rotation of the rotor 38 willeffect an equal displacement of the element 53.

The cooperating relationship of the several pump elements including therotor 38, the vanes 48, the non deformable member 51 and the nondeformable element 53 should now be considered for the purpose ofdeter..- mining the form of the present pump. From the showing in Figs.5, S-A and 5-B it will be noted that an outi pump or working chamber isformed between the inner cylindrical surface 52 on the element 53 andthe onter cylindrical surface of the hollow portion 41 of the rotor 38and in like manner an inner pump or working chamber is formed betweenthe outside diameter of themember 51 and the inside diameter of thehollow cylindrical portion 41 of the rotor 38.

The pumping operation of the device is effected by the displacement ofthe non-deformable element 53 and its associated parts from concentricrelationship with the axis of rotation of the rotor 38 and the amount ofeccentricity to one side of the concentric relationship will vary thedisplacement of the pump in one direction of discharge flow, while theamount of eccentricity of the other side of the concentric relationshipwill vary the pump displacement with the discharge of the pump flowingin the oppositedirection.

While any suitable adjusting means may be employed for varying thedisplacement of the pump and the direction of the pump discharge, in thepresent disclosure I have chosen to illustrate a means for effecting thealienate movement of the non-deformable member 51 and its associatedparts. This adjusting means comprises a stub shaft 54 mountedecceutrically with respect to the axis of rotation of a shaft 55 towhich it is secured. The shaft 55 is rotatably mounted in a bore 56formed in the ,Q Yer 29 and disposed eccentrically with respect to thecover portion 29. It should be noted that at this point that the axis ofrotation of the shaft 55 is slightly below the axis of rotation of therotor 38. The amount of offset of the stub shaft 54 with respect to theshaft 55 being substantially equal to the distance between therespective axes of the rotor shaft 39 and the shaft 55 so that thenorpdeformable ring member 51 and the non-deformable element 53 may bepositioned in concentric relationship with the rotor 38, in which thepump is in neutral or zero displacement position and from which it maybe movedin an arc to one side or the other to increase the displace:ment of the pump from zero to a maximum displacement regardless of thedirection of rotation of the rotor 38. The outer end of the shaft 55 isprovided with flat faces 57 adapted to receive a crank or adjustinghandle (not shown) by which the shaft 55 may be adjusted by partialrotation to move the stub shaft 54 into and out of .concentricrelationship with the axis of rotation of the rotor 38. A jamb nut 58 isthreaded on the shaft 55 and cooperates with a shoulder 59 formed on theshaft 55 to draw the shaft 55 outwardly so that the shoulder 59 bearstightly against a portion of the cover 29 to lock the stub shaft 54 indesired position with respect to the axis of the rotor 38. A pointer 60is secured to the shaft 55, in anyv appropriate manner, to provide avisual means for indicat ing the position of the stub shaft 54 withrespect to the axis of the rotor 38. Referring more specifically to Fig.2, the full line showing of the pointer 60 indicates the concentricrelationship of the stub shaft 54 with the of rotation of the rotor 38,wherein the cooperating 61;?

I 7 inents of the pump are in the position shown in Fig. 5. The dottedline showing of the pointer 60, shown to the left of the full lineshowing, indicates the maximum eccentricity of the ring member 51 withrespect to the rotor 38 wherein the several elements of the pump are inthe position shown in Fig. A of the drawings. In like manner, the dottedline showing of the pointer 60 to the right in Fig. 2 indicates themaximum eccentricity of the ring member 51 in the direction opposite tothat previously mentioned. The several elements of the pump thenassuming the position shown in Fig. 5B of the drawings.

A brief discussion of the arrangements of fluid passages and porting ofthe pump will now be described. As previously mentioned, the housingincludes a pair of chambers 22 and 23. The chamber 22 is provided with apair of threaded passages 61 and 62 either of which is adapted toreceive a pipe 63 or a pipe plug 64. The interchangeability of thepositioning of the pipe 63 and the plug 64 serves to simplify a pipingarrangement for connecting the pumpv into a working circuit. In likemanner, the chamber 23 is similarly provided with a pair of threadedports 65 and 66 which are adapted to selec tively receive either a pipe67 or a pipe plug 68 in a manner similar to that previously describedand for a like purpose. A passage or port 6? connects the chamber 22with the rotor recess and in like manner a port 70 serves to efiectcommunication between the chamber 23 and the rotor recess 25. Ports 71and 72 formed in a disc valve or distributor and collector disc 73connect respectively with ports 69 and 70 to direct fluid to or frompassages 74, 74' and 75, 75' respectively. Each of the passages 74, 74',75, and 75 (see Fig. 8) are arcuate in form and are disposed inconcentric relationship with a bore 76 formed in the plate 73. The bore76 being receivable on a hub portion 77 of the rotor shaft 39. The plate73 is secured in fixed position against the base of the rotor recess 25by means of a pair of dowel pins 78 which are secured in diametricallyspaced relationship in the base of the rotor recess 25 and are adaptedto receive bore 79 formed in the plate 73. The plate 4 3 of the rotor 38is provided with a plurality of circumferentially spaced ports 80 and80. The parts 80 being positioned to lie immediately adjacent the outersurface of each of the sectors 46 of the rotor 38; while the ports 8%)are disposed to lie immediately adjacent the inner surface of theseveral sectors 46 of the rotor 38. From the foregoing, it will be notedthat the passages and porting of the pump is simple in form and serve toprovide cooperating means through which fluid may be directed to andfrom the pump. Referring more particularly to Figs. 1, 5, 5A and 5 -Bwhen taken into conjunction with Figs. "i1 inclusive the followingdescription of the operation of the device will be clearly understood.At the outset of this description it should be understood that the rotor38 may be impelled selectively in either direction and in like manner,the position of the several cooperating pump elements ma be chan ed frommaximum eccentricit in one direc-' tion to maximum eccentricity in theother direction'or in any desired adjusted position between the twoextreme positions and including a central position wherein all of theparts of the pump are concentrically arranged with the resulting effectbeing a neutral or zero displacement position wherein the pump may besaid to be idling. Since the pump parts are free to rotate in eitherdirection and since the piping to and from the pump may be arranged inany suitable manner, the chambers 22 and 23 may be selectively chosenwith either as the inlet chamber with the remaining chamber servingasthe outlet chamber. For the purpose of the present description thechamber 22 will arbitrarily be taken as the inlet chamber and hencefluid from any suitable reservoir (not shown) maybe drawn into thechamber 22 through the intake .pipe 63., Under the rotary action of thepump fluid will be drawn from the chamber 22 through ports 69,71, andpassages 74 and 74 and thence through ports and 80' which are, at themoment, in communication with the respective passages 74 and 74'.Referring more particularly to Fig. 5-A, it will be noted that the rotor38 is turning in a clockwise direction and the degree of eccentricity ofthering member 51 is at an extreme position to the left of the neutralposition so that the volumetric capacity of the cylinders formed by theadjacent vanes 43 in the outer working chamber in cooperation with theinner cylindrical surface 52 of the ring 53 and the outer cylindricalsurface of the rotor sectors 46 are increasing in capacity duringone-half of the revolution of the associated pump parts and aredecreasing in capacity during the other half of the rotation of therotor 38; in like manner the similar cylinders formed by adjacent vanes48 in the inner working chamber in cooperation with the innercylindrical surface of the sectors 46 and the outer cylindrical surfaceof the element 53 function in the identical manner, just previouslydescribed, save for the fact that their action is oifset degrees withrespect to those in the outer pump. It will thus be seen that during theportion of rotation of the pump wherein the ports 3% and 80' formed inthe rotor 33 are in communication respectively with the passages 74 and74, fluid will be drawn into the expanding chambers and in like manner,during the remaining portion of a single rotation of the pump parts,fluid will be expelled from the decreasing capacity of the cylindersthrough the ports 8i? and 80' which are in communication with thepassages '75 and 75 and the fluid thus discharged from the decreasingcapacities of the cylinders will be directed through ports 72, 7%,outlet chamber 23, and into the pipe 67 which leads to the working sideof a circuit in which the pump is connected. With the above arrangementof ports and passages the combined capacities of both inner and outerpumps are utilized in the working circuit.

At this point it is deemed advisable to emphasize the fact that inactual pump operation the element 53, the several vanes 48 and themember 51 travel in the same direction and at the same speed of rotationas the rotor 38 with the result that sliding friction between theelement 53, vanes 4-8 and member 51 is reduced to a minimum and theefficiency of the pump is materially increased. The unitary rotation ofthe assembly comprising the element 53, the vanes =88 and the member 51is etfec'ted by the fact that the curved surfaces 54? of the vanes 42:

are respectively in line contact with the inner surface 52 cf theelement 53 and the outer cylindrical surface of the member 51. Thearrows on Figs. 5-A and 5-B indicating the direction of unitary rotationof the assembly comprising the element 53, the vanes 43 and the member51 under the influence of rotative movement of the rotor 38 whichincludes the hollow cylindrical flange portion 41 provided with slots 47to receive the several vanes 43 which retain the member 51 and element53 in concentric spaced. relationship.

As the form of the vanes 43 provide one of the principal reasons for thesuccessful and efficient operation of the present pump by reason of thefact that, in all positions of the adjustment between the rotor and theremaining operating parts of the pump, the curved or convex portion ofeach vane is retained in line contact with a cooperating element ormember of the unitary assembly independently of either hydraulic oryieldabie mechanical means. in addition to this important feature, thevanes are so constructed that the line of contact between them and theelement with which they cooperate is free to move on the convex surfaceof the vane as the amount of eccentricity between'the radial center lineof the vane and a radial line from the point of contact between theconvex surface of the vane and the cooperating element of the pump drawnto the axis of-the element form a common line at two positions in thecircumference of the element to positions substantially perpendicularto, the commonradial lines wherein the two radii form the greatest anglewith each other.

he. th s e h 1eeti9a. r feren e sheshi h ai t9 t estemmatie s ow ng i .5in wh h the n A in cates the .0 0J1 e ei-the tien 1% n ates. he g ea esdiver ence hetwee the two radii- Qhneu ly. th "m nt e eeh ae hetwe n thev ne 11 he ee peranng' el m nt w l 1 ve fern he e 2 rem posi ion nd ee 9PQSifiQI B 1e'side of the rete ra ius to. a similar extr me. 1:0... .11.01 th he side of t e 01 diu sinus hel ef a eve at on 0f the mint nd en eurn t the pesitie 1 de i e t remain n half o the ret re slh eh- .1 thishe ns it is c ea tha he l n o swtaee een ee between the vas a d t eeretias e em nt meve 'ever t eur eee 0 the' eh the ote; 38 hree e nn th.it th asseeia ee atient the m1. P wh ch nelude th v nes 48. he memb r5,1 an the element 5 The am u 1t 0f eeeht i h iress 9 member 5, enelemen 53 wi h eP'eet t6 th at ie ihe ee ed, 0n his. by the. le ter E- wth eteh t th e an 31 he eh i t fi e i 'ee ee 'he s tha the tsetse! mesurements 0m he in h e ee between he ot er F west su f ce 50 9 ehe 43.;or as e We e' ihslj e veee s use e3 he h ve shrt ee 5. e the element awhen eeeh es t1 f e Peh er the 911 1 e hte lihe'e th e seem e edi-he efitheeYlihQ iee eh teee 52 i he v a heated b the dimehei a s Ilse tee h...99? 9t th he e that slieeie r th s a eet is hee e 1 .1 911 lessee? ehe sthe; ma he 9 t ehsh e s e and nee he ee eeheiehle'r shew. f10111 e a 010011- teet between e serves shatese 'eithei e el01 te' 1 with the innercylindrical surface 52 of the ellement 53 e efieet 10111 t e eeht e t ese eee .52 th s perpend l ime f which te ht d w1 Pert 011 01 a chord 1,0f 1 ee e he e rt t n the ra us o the s reee ;fl e er h e t e d am t r ot e c nv x e fe 9f the n is ual 1 h hitt r ne be ween the radius m ofthe member 51 and the radius a of the element 5;; it will be jclear thata radial :drawn from the common center of the member 51 and element 53passing through the axis of the cylinder forming the convex surface ofthe vane will indicate that the vane surfaces 5.0 will lie in eorita ctwith the inner cylindrical surface 52 of the element 53 and also incontact .with the outer cylindrical surface of the member .51. Hence itwill be apparent that if this condition exists :in the extreme positionof eccentricity between the rotor 38 and the unit formed -by member 51,vanes 48, and element 53 it must also exist in all positions having alesser eccentricity. From the foregoing discussionfit will be apparentthat I have provided .a pump construction in which the operatingefiiciency of the device is maintained by the automatic compensation forvarying chordal positions of the vanes with respect to the surfaces withwhich the convex portions .of the vane contact during their eccentricrotation with respect to the rotation of the parts with which they aremaintained in constant surface contact. It should also be noted at thispoint that vanes of the present design'are adapted toma'intain theirdesired surface contact with the cooperating'parts of the pump withoutrequiring the inclusion of either hydraulic'pressure or yieldablemechanical means to elfect the desired result. A further advantage ofthe cooperative relationship between the several parts of the pump liesin the fact that the nicety of fit between the convex surfaces50 of thevanes and the cooperating surfaces of the element 53 and the member 51is such that all of the cooperating parts of the pump rotate as-a unitwith each part having the same angular velocity. By reason of this fact,it will be apparent that the emq ncy of the pump is greatly increaseddue to the practical elimination of s i in eh e wee the eeehiere i s eef9f t 1 11, 1

element 53 which efi ect s the increase of the capacity of the severalcylinders during one-half of a cycle of revolution and the decrease ofthe capacity of the sevcle of revolueral cylinders during the other halfof a cy tion to thereby elfect the intake of fluid by suction into theincreasing capacity of the cylinders while they are in communicationwith the intake passages 74 and 74 d ikew ie t the xh us ng 0f fluid ndP essure frornthe decreasing capacityof the cylinders when they are incommunication with the passages and 75.

Referring more particularly to Fig. 12 of the accompanying drawings itwill be noted I have illustrated a modified form of the valve ordistributor and collector plate 73 shown in Fig. 8. The modified formdiscloses a valve or distributor and collector plate 73 which isgenerally similar to the valve 73 except for the fact that the dischargeof the outer pump is directed into the intake sideof the inner pump withthe result that the pressure obtainable is substantially doubled sincethe unit new functions at a two stage compound pump. In order to insurethe obtaining of the maximumpressure in this pump arrangement, it shouldhe noted that the discharge of the pump having the greater volumetriccapacitl lis connected to theintake side of the pump having the'smallervolumetric capacity. It fshouldalso be understood that when the valve73' is substituted for the v 73 in the main pump showing that the pumpto" be effective only be rotated one direction, that is with the rotor32; turning in a clockwise direction wherein fluid is drawn into thepump through the ports 71 and intake passage 74 is discharged from theouter pump through the passage and intothe passage 7 4 through aconnecting passage 81. The discharge of the inner pump is directedthrough the passage 75 t0 the i se Pe t72 Ieferri ng more particularlyto Fig. 13 of the drawings it will be noted that another modified formof the valve .or dietributor plate 73 is shown, In the present modified1 elv 9. p t 73"1 s empleyed i h g nerall m a o m an rran ement w th thea ve e e 1 in his e e t 01 the e ha th 1 0 s e ee e e e a e a ran d nairne he t0 Pe mi th in e e d n o h dis arge t'th inne nd 00te1 Pumpe- Rfi r i 1 e p 1- 1leh t e 0 the 99 1 pah ins d aw n s i wi l h he d .1 1he e i t d 11 modifie 0 1 of pump .e ne heted in a r e ee w th the t ahihss .0 he a es ht i i 1 utilizing e n l ne ihs h mber- Thi e ifie01111 0f P11 119 is identical in operation and construction with thepumps previously described exceptfor the fact that only a single e ie 0fin ake and ou le ne te $9 er eq r h modified form of pump e bdying asingle working hamber l n s i s en eevel t e e pl d as a meter in whichinstance fluid under pressure delivered to the intake side of theunitprovides the motive power for fi ine t i .0. th H 1" d he ha 0f the ro omay b pnovid d th e pu le se 9. e he h (not shown) as a power take offmedium. to be used in any desired ma n Another, modified form of thepump construction is 48', which may be formed by appropriate lengths ofdrill rod having the correct diameter. These cylindrical'vanes 48' serveto replace the flat sided vanes 48 (previously described). The inclusionin this disclosure of four vanes in place of the six shown in theprevious form of the invention is purely arbitrary and of no realsignificance. Here again, the present modified form of pump can functionin the identical manner as previously described wherein the cooperatingparts of the pump rotate as a unit with the rotor 38 with each of theparts having the same angular velocity. However, the inclusion of thecylindrical vanes 48 in the present modification makes it possible torestrain either the member 51 or the element 53 against rotation withoutimpairing the efficient operation of the pump. This condition is madepossible by the fact that the cylindrical vanes 43 are free to revolveabout their axes and maintain a constant rolling contact with the fixedsurface 52 of the element 53 if this element is fixed against rotation,or maintain a constant rolling contact with the outer surface of themember 51 if this member be fixed against rotation. In either instance,it will be clear that the frictional resistance between the cooperatingparts of the pump will be reduced to a minimum by reason of the rollingcontact between the engaging surfaces of the relatively moving parts.

While the invention has been described in considerable detail in theforegoing specification, it is to be understood that various changes maybe made in its embodiments without departing from or sacrificing any ofthe advantages hereinafter claimed.

I claim:

1. In a pump the combination of a rotor including a hollow cylindricalflange portion, a non-deformable enveloping element surrounding theflange portion of said rotor, a cylindrical inner surface on saidnon-deformable element cooperating with the outer cylindrical surface onthe flange portion of said rotor to form an outer working chamber, anon-deformable member housed within the hollow portion of said rotor, acylindrical outer surface on said non-deformable member cooperating withthe inner surface on the hollow portion of said rotor to form an innerworking chamber, a plurality of one-piece vanes guided for radialsliding movement in the flange portion of said rotor, each of said vaneshaving oppositely disposed longitudinally extending cylindrical surfacescomprising parts of the surface of a cylinder having a diameter equal tothe difference between the radii of said cylindrical inner surface ofsaid element and said cylindrical outer surface of said member, saidoppositely disposed longitudinally extending cylindrical surfacesserving respectively to contact said inner cylindrical surface on saidnon-deformable element and said outer cylindrical surface on saidnon-deformable member to retain said element and member in unalterablespaced relationship; said vanes serving to divide each of said workingchambers into a plurality of cylinders, adjusting means for altering theposition of the common axis of said non deformable element andnon-deformable member with respect to the axis of said rotor to therebyvary the capacity of said working chambers and hence the displacement ofthe pump, means for effecting the rotation of said rotor, and fluidinlet and outlet means communicating with said working chambers wherebyrotation of said rotor effects the intake of fluid into the cylinderscornmunicating with said fluid inlet means and the discharge offluid-under pressure from the cylinders communicating with saidoutletmeans. V

2. In a pump the combination of a rotor including a hollow cylindricalflange portion, a freely rotatable nondeformable enveloping elementsurrounding the flange portion of said rotor, a cylindrical innersurface on said non-deformable element cooperating with the outercylindrical surfacelon the flange portion of, said rotor tojform anouter [working chamber, a-freely rotatable non deformable member housedwithin the hollow flange portion of said rotor, aqcylindrical outersurface on said nondeformable member cooperating with the inner surfaceofthe hollowlflange portion of said rotor to form an innerworkingchamber, a pluralityof one-piece vanes guided for radial slidingmovement in the flange portion of said rotor, each of said vanes havingoppositely disposed longitudinally extending cylindrical surfacescomprising parts of the surface of a cylinder having a diameter equal tothe difference between the radii'of said cylindrical inner surface ofsaid element and said cylindrical outer surface of said member, saidoppositely disposed longitudinally extending cylindrical surfacesserving respectively to contact said inner cylindrical surface on saidnon-deformable'element and said outer cylindrical surface on saidnon-deformable member to retain said elementand said member inunalterable spaced relation ship, said vanes serving to divide both ofsaid working chambers into a plurality of cylinders, adjusting means foraltering the position of the common axis of said nondeformable elementand said non-deformable member with respect to the axis of said rotor tothereby vary the capacity'of said working chambers and hence the displacement of the pump, driving means for elfecting rotation of saidrotor, vanes, non-deformable member and non-deformable element as a unitwith each part having the identical angular velocity whereby wearbetween the cooperating parts is materially reduced, and fluid inlet andoutlet means communicating with said working chambers whereby therotation of said rotor and associated parts eflects the intake of fluidinto the cylinders communicating with said fluid inlet means and thedischarge of fluid under pressure from the cylinders communicating withsaid fluid outlet means.

3. in a pump the combination of a rotor including a hollow cylindricalflange portion, a non-deformable enveioping element surrounding theflange portion of said rotor, a cylindrical inner surface on saidnon-deformable element cooperating with the outer cylindrical surface onthe flange portion of said rotor to form an outer working chamber, anon-deformable member housed within the hollow cylindrical flangeportion of said rotor, a cyrndrical outer surface on said non-deformablememcooperating with the inner surface on the flange portion of saidrotor to form an inner working chamber, a

'pluraiity of one piece vanes guided for radial sliding movement in theflange portion of said rotor, each of said Manes having oppositelydisposed longitudinaily exrding cylindrical surfaces comprising parts ofthe sure of a cylinder having a diameter equal the differbetween theradii of said cylindrical inner surface of aid element and saidCf/llldlijli outer surface of said member, said oppositely r. o edlongitudinally e nding'cylindrical surfaces serving re ely to consaidinner cylindrical surface on said no deformable rat and said outer cndrical surface on said nondcv rinable member to retain said element andsaid memher in unalterable spaced relationship, said serving to divideboth of said Working chambers into a plurality of cylinders, adjustingmeans for altering the position of the common of said element and saidmember selectively in opposite directions from concentric relationshipwith. the axis of rotation of said rotor to thereby effectre'rsai'of'the direction of flow of the pump output, ivit for effectingthe rotat of said rotor, and d inlet and outlet c'ommrnicating with bothof said working chambers whereby rotation of said rotor effects the offluid into'the cylinders communicatwith saidfluid inlet means thedischarge of fluid der pressure from the cylinders communicating withQuid fluid outlet means. I

4. A pump constructed as set forth in claim 3, in which the adjustingmeans for the position of the common of said non-deformable element andsaid non deformable member selectively in opposite directions fromconcentric relationship with the axis of said rotor is an asaas'e r 13eccentric arranged to impart acuate movement-of the common axis of saidelement and member through the axis of; said rotor. v p

5.- In a pump" the combination of a; rotor including a hollowcylindrical flange portion, a'freely rotatable nondeformable enveloping,element surrounding the flange portionof said rotor, acyli-ndrical-innersurface on said non-deformable element'cooperatingrwith the outercylindrical surface on the flange portion of said rotor to'form an outerworking chamber, a freely rotatable non-deformable member housed withinthe hollow cylindrical flange portion of said rotor, a cylindrical;outer surface on said non-deformable member cooperating with the innersurface of the hollow cylindrical portion of said rotor to form an innerworking chambeigla plurality of one-piece vanes guided for. radialslidingv movement in the flange portion of said rotor,=each ofsaidvaneshaving oppositely disposed longitudinally extending cylindricalsurfaces comprising partsof the surface of a cylinder having a diameterequal to the difference betweenthe radii of said cylindrical innersurface ofsaid element and said cylindrical outer surface of saidmember, said oppositely disposed longitudinally extending cylindricalsurfaces having serving respectivelyto contact said inner cylindricalsurface of said non-deformable element and said outer cylindricalsurface of said non-deformable member to retain said element and memberin unalterable' spaced relationship; said vanes serving to divide bothof said working chambersinto a plurality of cylinders, adjustingmeansfor altering the position ofthe common axis of said nondeformableelementand; said non-deformable member selectively in oppositedirections from concentric relationship with the ,ax-is of rotation ofsaid rotor to thereby effect the reversal of the direction of flow ofthe pump output, driving meansfor effecting the rotation of said rotor,vanes, member and element as a unit with, each part having the identicalangular velocity whereby wear on the cooperating parts of the pump ismaterially reduced, and fluid inlet. and outlet means communicating Withboth of said working chamberswhereby the rotation of said rotor and itsassociated parts effects the intake of fluid into the cylinderscommunicating with' said fluid inlet means and the discharge of fluidunder pressure from the cylinders communicating with said fluidoutletmeans.

6. A pump constructed as set forth in claim 5, in which the adjustingmeans fora-ltering the position of the common axis of saidnon-deformable element and said nondeformable member selectively inopposite directions from concentric relationship withlthe axis of saidrotor is an eccentric arranged to impartarcuate movement" of the commonaxis of said non-deformable element and said non-deformable memberthrough the axis of said rotor.

7. In a pump the combination of a rotor including a hollow cylindricalflange portion, a non-deformable enveloping element surrounding theflange portion of said rotor; a cylindrical inner surface on saidnon-deformable element cooperating with the outer cylindrical surface onthe flange portion of said rotor to form an outer working chamber, anon-deformable member housed within the hollow portionof said rotor, acylindrical outer surface onrsaid non-deformable member cooperating withthe inner surface on the flange portion of said rotor to form an innerworking' chamber, a plurality of one-piece vanes guiddfor radial slidingmovement in the flange portion of said rotor, each of said vanes havingoppositely longitudinally extending cylindrical surfaces comprisingparts of th'e surface of a cylin der having a diameter equal to thedifference between the radii of said cylindrical inn i surface of saidelement and said cylindrical outer surface of said member, saidoppositely disposed longitudinally extending cylindrical surfacesserving respectively 'to contact said inner cylindrical surface on saidnon-deformable "element and said outer cylindrical surface onsaidnon-deformabIe member to "retain said element and member inunalterable spaced relationship; said vanes.v serving, to divide both ofsaid workingchambers into' a plurality of cylinders, adjusting means foraltering thepo'sition of the common axis. of said element and. said.member selectively in opposite directions from concentric relationshipwith the, axis of rotationof said rotor to thereby effect reversal ofthe direction offlow of thepumpoutput andvary the capacity of theworking chambers to. vary the displacement of the pump, driving'meansfor effecting therotation of said rotor, and fluid inlet and outlet.means, communicating with both of. said workingchamberswhereby rotationof said, rotor effects the. intake of fluid into the cylinderscommunicatingwith. saidfluid inlet means and the discharge of fluidunder pressure! from't-hecylinders com.- municating/with said fluidoutlet means.

8. A pump constructedas set forth in claim 7, in which the cooperating.pump parts including said rotor, vanes, non-deformable element andnon-deformable member rotate as a unitwitheach parthaving the identicalangular. velocity Wherebywear on the cooperating parts, of the pump arematerially reduced.

9. A. pump constructed. as set forth in claim 7, in which the adjusting;means for altering the position of the common a-xis ofsaidnonsd'eformable element and said nondeformablemember selectively inopposite directions from concentric relationship with the axis of saidrotor is an eccentric arranged, to impart arcuate movement to the commonaxis. of said element and said. member through the axis of said rotor.-

10. In a rotary pump the combination with a rotor including a hollowcylindrical flange portion, a plurality of radially disposed vane"receiving slots in the flange portion. of saidrotor, non-deformableenveloping element surrounding the flange portion of said. rotor havinga cylindrical inner surface. cooperating with the outer cylindricalsurface. of said rotor to form an outer Working chamber, anonrdeforma'ble member housed within said hollow cylindrical portion ofsaid rotor having a cylindrical outer surface cooperating with the innersurface of the flange portion of said rotor to form an inner workingchamber, a plurality of one-piece vanes each comprising a quadrilateralprism including a pair of parallel flat sides and. a pair of convexlongitudinally extending parallel faces formed by portions of thesurface of a cylinder having a diameter equal to the difference betweenthe radii of said, cylindrical inner surface of said element and saidcylindrical outer surface of said member, each of said vane receivingslots in said rotor adapted to cooperate with the flat sides on one ofsaid vanes to position and guide the same for radial sliding movement inthe flange portion of said rotor, said convex faces of said vanesserving to retain said element and member in unalterable spacedrelationship with one convex face of each of said vanes having constantline contact with the inner cylindrical surface of said non-deformableelement and the opposite convex face of each of said vanes havingconstantline contact with the outer cylindrical surface of saidnon-deformable member, said vanes serving to divide both of said workingchambers into a plurality of cylinders, means for adjusting theeccentricity of said unit-deformable element and said nondeformablemember as a unit with respect to the axis of rotationof said rotor tothereby simultaneously vary the capacity of both of said workingchambers and the- 15 V angular velocity whereby wear on thecooperatingparts of the pump is materially reduced.

12. A pump constructed as set forth in claim 16, in which the adjustingmeans for altering the position of the common axis of saidnon-deformable element and said non-deformable member selectively inopposite directions from concentric relationship with the axis of saidrotor is an eccentric arranged to impart arcuate movement to the commonaxis of said element and said member through the axis of said rotor.

13. In a pump the combination of a rotor including a hollow cylindricalportion, a non-deformable envelop ingelement surrounding the hollowcylindrical portion of said rotor, a cylindrical inner surface on saidnon-deformable element cooperating with the outer cylindrical surface onhollow cylindrical portion of said rotor to form a working chamber,anon-deformable member housed within the hollow portion of said rotor, aplurality of one-piece vanes arranged for radial sliding movement in thehollow cylindrical portion of said rotor, said vanes each including apair of longitudinally extending parallel cylindrical surfaces formed byportions of the surface of a cylinder having a diameter equal to theditference' be tween the radii of said cylindrical surface of saidelement and said cylindrical outer surface of said member, saidlongitudinally extending parallel cylindrical surfaces of said vanesserving to provide a means by which said element member are retained infixed spaced relationship by being disposed between said non-deformableenveloping element and said non-deformable member and having constantsurface contact with said inner cylindrical surface of saidnon-deformable element and the outer cylindrical surface of saidnon-deformable member, said vanes serving to divide said working chamberinto a pinrality of cylinders, said non-deformable element and saidnon-deformablemet'nber having a common axis offset from the axis of saidrotor to control the volumetric displacement of said pump, adjustingmeans for altering the position of the common axis of saidnon-deformable element and said non-deformable member with respect tothe axis of said rotor, driving means for effecting the rotatlon of saidrotor, and fluid inlet and outlet means communicating with said workingchamber whereby rotation of said rotor elfects the intake of fluid intothe cylinders communicating with said fluid inlet means and thedischarge of fluid under pressure from the cylinders communicating withsaid outlet means.

14. A pump constructed as set forth in claim 13, in which thecooperating pump parts including said rotor,

vanes, non-deformable element and non-deformable member rotate as a unitwith each part having the identical angular velocity whereby Wear on thecooperating parts of the pump is materially reduced.

15. A pump constructed as set forth in claim 13, in which the adjustingmeans for altering the position of the common axis of saidnon-deformable element and said non-deformable member with respect tothe axis of rotation of said rotor is an eccentric arranged to impartarcuate movement of the common axis of said element and member throughthe axis of said rotor.

16. In a pump the combination of a rotor including a hollow cylindricalportion, a non-deformable enveloping element surrounding the hollowcylindrical portion of said rotor, a cylindrical inner surface on saidnon-deformable element cooperating with the outer cylindrical surface onthe hollow cylindrical portion of said rotor to form a working chamber,a non-deformable member housed within the hollow cylindrical portion ofsaid rotor, a plurality of one-piece vanes arranged for radial slidingmovement in the Wall of the cylindrical portion of said rotor, saidvanes each including a pair of longi tudinally extending parallelcylindrical surfaces formed by portions of the surface of a cylinderhaving a diameter equal to the diflerence between the radii of saidinner; cylindrical surface of said element and said outer cylindricalsurface of said member, said longitudinally extending parallelcylindrical surfaces of said vanes serving to provide a means by whichsaid element and member are retained in fixed spaced relationship bybeing disposed between said non-deformable enveloping element and saidnon-deformable member and having constant surface contact with saidinner cylindrical surface of said noneformable element and the outercylindrical surface of said non-deformable member, said vanes serving todivide said working chamber into a plurality of cylinders, saidnon-deformable element and said non-deformable member being retained incoaxial position by said vanes, adjusting means for altering theposition of the common axis of said element and said member with respectto the axis of said rotor, driving means for effecting the rotation ofsaid rotor, and fluid inlet and outlet means communicating' with saidworking chamber whereby rotation of said rotor effects the intake offluid into the cylinders communicating with said fluid inlet means andthe discharge of fluid under pressure from the cylinders communicatingwith said outlet means.

17. A pump constructed as set forth in claim 16, in which thecooperating pump parts including said rotor, vanes, non-deformableelement and non-deformable member rotate as a unit with each part havingthe identical angular'velocity whereby wear on the cooperating parts ofthe pump is materially reduced.

18. A pump constructed as set forth in claim 16, in which the adjustingmeans for'altering the position of the common axis'of saidnon-deformable element and said non deformable member selectively'inopposite directions from concentric relationship with the axis of saidrotor is an eccentric arranged to impart arcuate movement of the commonaxis of said non-deformable element and non-deformable member throughthe axis of said rotor.

19. In a pump the combination of a rotor including a hollow cylindricalportion, a non-deformable envelop.- lng element surrounding the hollowcylindrical portion of said rotor, a cylindrical inner surface on saidnondeformable element cooperating with the outer cylindrical surface onthe hollow cylindrical portion of said rotor to form a working chamber,a non-deformable member housed within said rotor, a plurality ofone-piece vanes arranged for radial sliding movement in the wall of thehollow cylindrical portion of said rotor, said vanes each including apair of longitudinally extending parallel cylindrical surfaces formed byportions of the surface of a cylinder having a diameter equal to thedifference between the radii of said inner cylindrical surface of saidelement and said cylindrical surface of said member, said longitudinallyextending parallel cylindrical surfaces of said vanes serving to providea means by which said element and member are retained in fixed spacedrelationship by being disposed between said non-deformable envelopingelement and said non-deformable member and having constant surfacecontact with said inner cylindrical surface of said non-deformableelement and the outer cylindrical surface of said non-deformable member,said vanes serving to divide said working chamber into a plurality ofcylinders, said non-deformable element and said non-deformable memberbeing retained in coaxial position by said vanes, adjusting means foraltering the position of the common axis of said non-deformable elementand said non-deformable member selectively in opposite directions fromconcentric relationship with the axis of rotation of said rotor tothereby etfectreversal of the direction offlow of the pump output andvary the capacity of the working chambers to'vary the displacement ofthe pump, driving means for effecting the'rota: tion of said rotor, andfluid inlet and outlet means communicating with said Working chamberwhereby rotation of said rotor effects the intake of fluid into thecylinders communicating with said fluid inlet, means and the dis chargeof fluid under pressure from the cylinders communicating with said fluidoutlet means.

20. A pump constructed as set forth in claim 19, in which thecooperating pump parts including said rotor, vanes, non-deformableelement and non-deformable member rotate as a unit with each part havingthe identical angular velocity whereby wear on the cooperating parts ofthe pump are materially reduced.

21. A pump constructed as set forth in claim 19, in which the adjustingmeans for altering the position of the common axis of saidnon-deformable element and said non-deformable member selectively inopposite directions from concentric relationship with the axis of saidrotor is an eccentric arranged to impart arcuate movement to the commonaxis of said non-deformable element and said non-deformable memberthrough the axis of said rotor.

22. In a rotary pump the combination of a rotor including a hollowcylindrical portion, a plurality of radially disposed vane receiving andguiding slots in the wall of the cylindrical portion of said rotor, anon-deformable enveloping element surrounding the hollow cylindricalportion of said rotor, an inner cylindrical surface on saidnon-deformable element cooperating with the outer surface on the hollowcylindrical portion of said rotor to form a working chamber, anon-deformable member having a cylindrical outer surface housed withinsaid rotor, a plurality of one-piece vanes each comprising aquadrilateral prism including a pair of parallel flat sides and a pairof longitudinally extending parallel convex faces formed at portions ofa cylinder having a diameter equal to the difference between the radiiof said cylindrical inner surface of said element and said cylindricalouter surface of said member, each of said vane receiving slots in wallof the hollow cylindrical portion of said rotor adapted to cooperatewith the flat sides on one of said vanes to position and guide the samefor radial sliding movement in the wall of the hollow cylindricalportion of said rotor, said longitudinally extending parallel convexedfaces of each of said vanes forming a means for retaining said elementand said member in fixed spaced relationship by having one convex faceof each of said vanes having constant line contact with the innercylindrical surface of said non-deformable element and the oppositeconvex face of each of said vanes having constant line contact with theouter surface of the said non-deformable member, said vanes serving todivide said working chamber into a plurality of cylinders, adjustingmeans for altering the position of the common axis of saidnon-deformable element and said non-deformable member as a unit withrespect to the axis of rotation of said rotor to thereby simultaneouslyvary the capacity of said chamber and the displacement of the pump,driving means for effecting the rotation of said rotor, and fluid inletand outlet means communicating with said working chamber wherebyrotation of said rotor effects the intake of fluid into the cylinderscornmunicating with said fluid inlet means and the discharge of fluidunder pressure from the cylinders communicating with said outlet means.

23. A pump constructed as set forth in claim 22, in which thecooperating pump parts including said rotor, vanes, non-deformableelement and non-deformable member rotate as a unit with each part havingthe identical angular velocity whereby wear on the cooperating parts ofthe pump is materially reduced.

24. A pump constructed as set forth in claim 22, in which the adjustingmeans for altering the position of the common axis of saidnon-deformable element and said non-deformable member with respect tothe axis of rotation of said rotor is an eccentric arranged to impartarcuate movement of the common axis of said non-deformable element andnon-deformable member through the axis of said rotor.

References Cited in the file of this patent UNITED STATES PATENTS1,468,889 Trotter Sept. 25, 1923 1,607,383 Aurand Nov. 16, 19262,256,099 Mayer Sept. 16, 1941 2,266,191 Granberg Dec. 16, 19412,280,626 Carpenter Apr. 21, 1942 2,354,076 Tucker et a1. July 18, 19442,368,572 Say Jan. 30, 1945 2,458,023 Pike Jan. 4, 1949 2,469,097 WrennMay 3, 1949 2,494,884 Lassmann Jan. 17, 1950 2,531,861 Schmitt Nov. 28,1950 2,543,603 Schatzel Feb. 27, 1951 2,552,860 Oliver May 15, 19512,592,247 Coe Apr. 8, 1952 2,635,551 DeLancey Apr. 21, 1953 2,646,004Bergen July 21, 1953 2,649,739 Hufferd et al. Aug. 25, 1953 2,678,607I-Iutferd et a1. May 18, 1954 FOREIGN PATENTS 596,902 Great Britain Jan.13, 1948 OTHER REFERENCES Ser. No. 239,352, Sturm (A. P. C.), May 11,1943.

